Multiple delivery liquid pump



Nov. 21, 1933.` L, LE BRET Er AL 1,936,169

MULTIPLE DELIVERY LIQUID PUMP Filed July 5. 1930' 2 sheets-snee*k 1 A.Nm-f. 21, 19133. LE BRET Er AL 1,936,169

MULTIPLE DELIVERY LIQUID PUMPv YPatented Nov. 21, 1933 UNITED STATI-:s PArENr orales A i i 1,9as,is9- y A MULTIPLE 'DELIVERY LIQUID PUMP Ludwig' le Bret, Berlin-Charlottenburg, and

. Gnther Appliance-Jung, 1930. semi J v iz claims.

This invention relates to a pump for supplying fuel, oils, lubricants, water injection to a plurality of consumption places, as described and shown in the U. S. A. Patent No. 1,568,170, in which it isa question of accurately measuring the quantities of liquid for each individual point of use by only one single operating piston.

The fundamental feature of 4the invention is that the reciprocating piston movement is obtained by means of only two stroke pins sliding on helicalor similarly shaped guide faces, one of which pins owing to its semi-circular crosssection does not touch the induction cam race.- whereas both simultaneously bear against the compression cam race. The strokeA pi'ns are arranged on the guide piston which is rotatably and shiftably guided vertically in a cylindrical bore. The working piston is suspended for this purpose in a T-groove of the guide piston, which groove is situated on the side directed towards the control valve. By this means only axiallyA directed forces are exerted on the operating piston owing to the articulated connection with the guide piston. A wedge-shaped clutch claw transmits, through a clutch projection on the control valve, the turning movement of the operating piston suspended thereon to the guide piston. The vertical symmetry plane passing through the axis oi the stroke pin and through the front of the clutch claw coincides with or forms an extension of the vertical plane through the centralA axis oi' the guide piston. The symmetry planes of the clutch projection and of the control channel of the control piston coincides.

'Ihe invention is further characterized in that the stroke pin moves always the same distance in advance of the control channel with left hand drive as well as at right hand drive, so that always the same suction segment each exhaust irrespective of the direction of rotation. Moreover, the .control valve has onlyone control channel, which connects the cylinder space alternately with the induction Aand compression'pos of the control sleeve. vA further feature consists in that a circulation channel adapted to communicate with the control channel establishes together witha circulation channel in thecontrol sleeve the connection between the control channel and the induction ports.

Constructions are known in single piston pumps, in which two stroke pins are employed Vfor effecting the piston stroke. However in the known construction a rotary cam with only two cam races is employed, which during its rotation eiects the induction stroke of the operatini Sehneggenburger,

. ment a stroke pin of the control valve and.

race would not be ensured. Alin order to allow for effects the suction for ylatably connected together,

Berhn-Halensee,

(ci. 10a-z) piston through the intermediary-of a nonrotat-4 able ring shiftable in the direction of the stroke and connecting the cam positively but not rigidly Ato the. piston by means of stroke rollers, the compression stroke being eiected by a piston spring and not by cam parts sliding on one another. A rotating disc control valve with only onecontrol channel is employed and the guidepiston is connected to the operating piston vby a ball-like s connection.

Constructions are also known of single piston pumps with a plurality. of points o f consumption, distribution being Aeffected by a rotating barrel with a single control channel. The reciprocation of the parts is eiected by means of a lever pivoted to the head o! the barreL-one end of the lever sliding in a cam groove and the other engaging the plunger. As distinguished from this arrange-l moving parallel to its axis is to the invention instead of a u employed according lever.

The features of the present invention represent considerable improvements as compared withA the construction hitherto known, which improvements are directed chiefly to simple manufacturing and to the suitability of the'pump for higher pressures.

In the rigid connection of the operating piston with the stroke disc, according to U. S. A. Patent 1,568,170, it was necessary for the cylinder bore of the pump to register most accurately with the compressioncurve for a thousandth of a millimeter, as otherwise a simultaneous bearing of the stroke pins on the .compression cam these inaccuracies, which might occur in the manufacture, a number of stroke pins, corre sponding to that of the curve race segments,4 were provided on the stroke disc of the piston. By this .means at least. three of the six stroke pins were at the same time in contact with the compression cam race, and consequently not too great bending stresses were exerted on the operating piston. This however only represented a provisional solution, which was not sulcient'for high pump pressures, such as are requiredtoday.' For overcoming these objections the stroke pins have, according to the invention, been separated from the operating piston and are only oscilinv order to relieve the operating piston from any bending stress inthe event of one sided bearing of the stroke pins. It is thus possible to usea smaller number of stroke pms.' 'me stroke-pms are riaidlr mounted l."

in a separate guide piston, which in turn is guided in a cylindrical guide. The operating piston is hingedly connected with the guide piston in such a manner that it is axially movable without play, whereas it is laterally movable in all directions towards the side of and at an angle to the axial direction. Consequently only forces 'acting in axial direction can exert themselves on the operating pistons and, as bending forces no p longer act on this piston, pistons can be used which are of very small diameter. A

The coupling of the guide`piston with the rotary driving control valve is effected by two clutch projections on these elements. The clutch `is further so constructed that, at right hand or left hand driving of the control slide, the same induction element always eiects the induction stroke for supplying the discharge situated thereunder. The coupling of these two parts is therefore so constructed that the solid stroke pin effecting the induction stroke always moves a small angle in advance of the control channel in the control valve, in order to fuliill the above mentioned condition. Consequently these clutch projections, according to the invention, are made wedge-shaped, as this shape offers the greatest material cross section for the small angles of oscillation available. Moreover, this wedgeshaped form of the clutch projections causes a reaction on the control valve through the clutch forces which arise. This reaction causes the control channel of the control valve and its immediate surroundings situated under the .clutch projection to bear fully against the control sleeve so that a packing pressure is produced preventing losses due to leakage during the compression stroke. Consequently, a better volumetric degree of eiliciency is obtainable with higher pump pressures.

-been considerably reduced.

In order to further improve the volumetric degree of eniciency, the pump control has also been considerably improved. `The number of control channels has been reduced from two to only one and consequently the noxious cylinder space has This is important for obtaining-a better induction eiect with viscous driving media. The control channel connects, during the compression stroke, the cylinder space directly with the actual compression port iu the control sleeve, whereas during the induction period two circulation channels, one in the control valve and the other in the control sleeve, serve as connection between the control channel and the actual induction port in the control sleeve. By means of these circulation channels the registering portions between control channel and the induction ports in the control valve during the compression stroke are triplicated. The diameter of the control valve remains the same, as the pressure liquid must pass from the control channel to the circulation channel inthe control sleeve, from vthis into the circulation channel in the control valve, and thence to the induction port in the control sleeve. Without pressures, pump pressures approximately three times as great'are obtained by this feature of vbeing for turning the invention with the same volumetric degree of eniciency.

An embodiment of the invention is illustrated by way of example in the accompanying drawings in which:

Fig. 1 is a cross section through the pump.

Fig. 2 is a vertical section of Fig. 1.

Fig. 3 shows a section on line III-III of Fig. l.

Fig. 4 shows a section on line IV-IV of Fig. l.

Fig. 5 is a diagrammatic view of the control, the cam groove and the inner casing surface of the control sleeve being shown in development.

In the casing 23 the control valve 3 rotates always at the same angle a between stroke pins 6 in advance of the direction of movement lndependently of the direction of rotation through the intermediary of the worm gear 1, 2. In the axis of the valve, a cylinder 25 is provided with operating piston or compressor 4, which isoscillatably suspended by means of a T-groove 24 in the guide piston 5 situated thereover.

The control valve 3 has a catch l0 on its upper end, which bears against a wedge-shaped nose 9 on the lower part of the guide piston 5 in such a manner that, on the rotation of the control valve 3 the guide piston 5 is also rotated. Ay stroke bolt 6 is mountedin a b`ore perpendicular to the axis of rotation in the guide piston 5, the ends 6', 63 of which bolt project laterally from the guide piston. The end of stroke pin 62 is a half pin. These two stroke pins 6 and 62 extend into a cam groove formed by cut out portions in the upper compression curve 7 and by a' plurality of independently movable suction cam segments 8, arranged under the upper compression curve 'I and adjustable by means of a spindle 21 and set nut 22. The control valve 3 is surrounded by a stationary control sleeve 13 having bores for the control corresponding in their arrangement exactly:to the rising and falling curves of the cam groove. An induction line 19 and discharges 14 ing points of` lubrication are arranged in the caslng 23.

Fig. 5 shows the effect of the advance movement of the stroke pin 6' relative to the control channel 11 on the independency of the direction of rotation in order that-the same induction seg-v ment 8 shall effect the induction stroke for supplving the pressure port 12. This gure also shows the effect of the circulating channels 15, 16 on the packing covering between the suction port 17 and the pressure .port 12 in the control sleeve 13.

The upper part of Fig. V5 shows the development of the curve 7 and segments 8 with the stroke pins 6' in various positions therein. The lower part of this figure shows the development of th control sleeve 13 and the control'channel 11 and the circulating channel 16 (shown in dotted lines) arranged'in the control valve 3, also in different positions. l The independency of the stroke pins 6', the co' trol channel 11, and circulating channel 16 are shown at the beginning of the induction stroke and at the end of the pressure stroke, vthe left portion of the figure to theright and the right portion for turning to the left.

Only the complete stroke pin 6. is shown as it slides through the curve 7 as this effects both the induction and the pressure sponsible for the control. The half stroke pin. 6? only bears on the race of the pressure curve and then always together with the stroke pin 6' but always on the opposite side of the pressure stroke and is re- `stroke pin 6' is indicated curve arranged in a circle. The'path' of the 'for both directions of rotation.

During the turning to the right (left portion of the ngure) the control channel 1l in the control valve 3 sucks from the suction port 17 situated on the left under the suction segment,

' whereas thestroke pin 6' eiects the induction stroke of the operatingfpiston 4 by sliding upwards on the 'left curve race of the suction segment 8. The stroke pin-6' as shown moves a Acertain distance in advance of the control chan- During the downward movement of the stroke pin 6', that is during the pressure stroke, the control channel 11 comes to register 'with the pressure port 12 situated under the controlling suction segment 8. y

During the turningto the left (right portion nel 1l.

I of the figure) the stroke pin 6' again moves in instance towards the left.

ing the rotation to the right suction segment 8 effects the suction stroke by advance of the control channel 11 but in this During this direction of rotation the suction is eiected from the suction port 1'1 situated on the right under the controlling suction segment 8 during the upward of the curve effecting the induction and pressurestrokes are indicated by cross-hatching. Durthe left curve of the the upward movement of the stroke pin 6', whereas the right portion of the pressure) curve 'I effects the pressurel stroke by the downward movement o1 the stroke pin 6'.

During the rotation to the left the opposite sides ofthe curves to those marked by crosshatching effect the induction and pressure strokes.

The circulating channel 15 in In Fig. 5 on the right at the top an entirely lowered suction segment 8 isshown in dotted lines. The stroke pin 6 in this position slides over the suction segment without being raised and consequently without imparting a suction stroke to'the operating piston 4. Consequently at4 this point no pressure stroke willioccur and no-feed medium supplied to the pressure port under this suction segment.

the control sleeve 13 and the circulating channel 16 in the rotary control valve 3 establish communication between the suction portfl'i and the control channel 11 during the induction period. The control channel 11 is arranged on a diierent plane to the suction port 1'1 in the control sleeve; During the induction stroke the conveying medium is supplied bythe suction underpressure occurring 'in the cylinder from the suction port 17-to the con-4 trol channel 11 through the'registering circuv lating channels- 16, 15. .During the pressure stroke however the medium is supplied from the control channel 11 directly to the pressure por 12 of the control sleeve. In the right portion of Fig. 5 is shown diagrammatically by means-of arrows 1, 2, and 3 the path which a portion of the 'conveying edium must ollow at the end of the pressure stroke, which medium does not come into the pressure line -at Alow degree of efficiency- This lostl conveying medium which does not pass into the pressure line must pass from the control charmel l1 to the tion channel 16 in the control valve 3 with a succirculating channel 15 at 1, thence .tothe circulating channel 16 at 2 and finally romhere to the suction port 1'1 at 3.

The operation is as follows:-

The control valve 3 with the operating piston 4 is rotated by the worm gearing 1, 2.2 The clutch projection 10 of the control valve bears against the nose 9 of the guide piston 5 and rotates same. The stroke pins 6 and 62 of the stroke bolt 6 of the guide piston 5 engagewin cavities of the upper compression cam 7 and run on the rising and descending portions of the cam groove through the rotation of the guide piston 5 so that the guide piston 5 and operating piston 4 are moved up `and down. T he upward movement of the piston 4 constitutes the induction stroke and the downward movement the compression stroke.

During the downward movement, that is during the compression stroke, the cylinder space 25 is connected with the outlet 14,y leading to the corresponding lubricating point, by means of a control channel 11 of the control valve 3 and a corresponding pressure port 12 of the controlsleeve 13 (Fig. 1) .A

During the upward movement, that is. at the suction stroke of the piston 4, the cylinder-space 25 is connected by means of a control channel 11 \of the control valve 3 'and a circulating channel 15 o'f the control sleeve 13 by meansvvof a circulation port 17 of the control sleeve, which is connected by a collecting groove 20 with the suction pipe 19 (Fig. 2). The bores of the control sleeve 13 for the control are arranged according to the rising and falling curves of the cam groove. The piston 4 therefore always sucks from the common induction pipe 19, but delivers the sucked in liquid consecutively to the outlets 14 of the casing 23. The solid stroke pin 6 of the stroke bolt 6 controls alone the induction stroke, as the other stroke pin 62, constructed as a half pin is always situated above the suction elements 8 without however touching these. If a suction segment 8 is for example lowered by the adjusting device 21, 22, ajshorter induction stroke of the piston 4 120 is obtained at this point so that the corresponding outlet 14 will receive less liquid. Consequently each individual outlet can be adjusted as regards the quantity supplied between zero and maximum independently of the others. We claimz- 1. In a pump for delivering'liquid to a plurality of consumption places the combination of an operatingpiston, a control valve surrounding and adapted to rotate with said operating piston, strokepins above said control valve, means for connecting said pins to said operating piston, and means for etecting the reciprocating motion of said operatingpiston and the inductionr and compression stroke of said operating piston through the intermediary of s'aid stroke pins.

2. In a pump for delivering liquid to a plurality of consumption place the combination of an operating piston, a control valve surrounding and adapted to rotate with said operating piston, two stroke pins of different cross sectional areas above said piston, a'cam drive having suction vcam races, with which only the pin of larger' cross sectional area engages, and compression and having 'a control channel, stroke pins above 150 said control valve one of said pins of larger cross sectional area than the other, means for connecting said pins to said operating piston, a casing surrounding said control valve having a plurality of outlets leading to the different consumption. places, a cam drive adapted to effect the reciprocating motion of said piston and the induction and compression stroke of said operating -piston through the intermediary of said stroke pins, and induction segments on said cam drive adapted to coact with the stroke pin of larger cross sectional area moving at a like angle in advance of said control channel to cause said induction stroke for its co-ordinate outlet irrespective of the direction of rotation.

4 A pump for delivering liquid to a plurality of consumption places, comprising in combination an operating piston, a control valve surrounding and adapted to rotate with said operating piston, stroke pins above said control valve, means for connecting said pins to said'operating piston, means for effecting the reciprocating motion of said piston and the induction and compression'stroke through the intermediary of said eol stroke pins, a casing surrounding said control valve having suction and pressure ports, said control valve having only one control channel adapted to connect the space in said casing alternately with the suction and pressure ports of said casing.

5.-A pump for delivering liquid to a plurality of consumption places, comprising in combination an operating piston, a control valve surrounding and adapted to rotate with said operating piston, stroke pins above said control valve,

means for connecting said pins to said operatingA piston, means for eiecting the reciprocating motion of said piston and the induction and compression stroke through the intermediary of said stroke pins, a casing surrounding said control valve having suction and pressure .ports and a circulating channel, said control valve having a control channel and a circulating channel adapted toco-operate with the circulating channel in said casing to establish the connection with the suction ports in said casing.

6. In a pump for delivering liquid to a plurality' of consumption places the combination of an operating piston, a control valve surroundingand adapted to rotate with said operating piston, a guide piston above said operating piston, means for transmitting the rotary movement of said valve to said guide piston, stroke pins projecting from said guide piston, and means for effecting. ythe reciprocating motion of said pistons and the induction and compression stroke of said operating pistonv through the intermediary of said stroke pins.

7. In a pump for delivering liquid to a plurality of consumption places the combination of an operating piston, a control valve surrounding and adapted to rotate with said operating piston, a.v

guidek piston above said operating piston, stroke pins projecting from said guide piston, and a casing having a cylindrical bore adapted to rotatably and shiftably guide said guide piston, said stroke pins adapted to guide said operating piston in axial direction.

8. In a pump for delivering liquid to a plurality of consumption places the combination of an operating piston, a control valve surrounding and adapted to rotate with said operating piston, a' guide pisto'nabove said operating piston, said operating piston hingedly connected and laterally shiftable relative to said guide piston, to allow forces to be exerted on said operating piston only in axial direction, stroke pins projecting from said guide piston, and means for eiecting the reciprocating motion of said pistons and the induction and compression stroke of said operating piston through the intermediary of said stroke pins.

9. In a pump for delivering liquid to a plurality of consumption places the combination of an operating piston, a control valve surrounding and adapted to rotate with said operating piston, a guide piston above said operating piston having a T-groove on the side directed towards said control valve adapted to oscillatably support said operating piston, stroke pins projecting from said guide piston, and a casing having a cylindrical bore adapted to rotatably and shiftably guide said guide piston, said stroke pins adapted to guide said operating piston in axial direction.

l0. In a pump for delivering liquid to a plurality of consumption places the combination of an operating piston, a control valve surrounding and adapted to rotate with said operating piston, a guide piston above said operating piston, a clutch projection on said valve, a wedge-shaped nose on said guide piston engaging said clutch projection adapted to transmit the rotary movement of said control valve and of said operating piston to said guide piston through the intermediary of said clutch projection, stroke pins projecting from said guide piston, and means for effecting the reciprocating motion of said pistons and the induction and compression stroke of said operating piston through the intermediary M0 of said stroke pins. u

ll. In a pump for delivering liquid to a plurality of consumption places the combination of an operating piston, aA control valve surrounding and adapted to rotate with said operating piston, a clutch on said valve, a guide piston above said operating piston, a nose on said guide piston engaging said clutch projection, a nose on said guide piston engaging said clutch projection adapted to transmit the rotary movement of 120 said valve to said guide piston, stroke pins projecting from said guide piston one of said stroke pins being of larger cross sectional area than the others and situated with said clutch projection in a plane passing through the central axis of said i125 guide piston, and means for eiecting the reciprocating motion of said operatnig piston and the induction and compression stroke of said operating piston through the intermediary of said stroke pms.

12. In a pump for delivering liquid to a plu- Vrality of consumption places the combination of an operating piston, a control valve surrounding and adapted to rotate with said operating piston and having a control channel,`a clutch projection on said valve, the centre-of said control channel lying with said clutch projection in a plane through the central axis of said control valve, a nose on said guide piston engaging said LUDWIG Lr. BRET. G SCHNEGGENBURGER. 

